US3694107A - Ejector apparatus and method of utilizing same - Google Patents

Ejector apparatus and method of utilizing same Download PDF

Info

Publication number
US3694107A
US3694107A US3694107DA US3694107A US 3694107 A US3694107 A US 3694107A US 3694107D A US3694107D A US 3694107DA US 3694107 A US3694107 A US 3694107A
Authority
US
Grant status
Grant
Patent type
Prior art keywords
fluid
stream
nozzle
motive
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
Inventor
Robert Stein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nash Engineering Co
NASH ENG CO
Original Assignee
Nash Engineering Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Grant date

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46Arrangements of nozzles
    • F04F5/467Arrangements of nozzles with a plurality of nozzles arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46Arrangements of nozzles
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46Arrangements of nozzles
    • F04F5/466Arrangements of nozzles with a plurality of nozzles arranged in parallel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46Arrangements of nozzles
    • F04F5/469Arrangements of nozzles for steam engines

Abstract

A compound ejector apparatus comprising a primary nozzle, primary mixing chamber, secondary nozzle, secondary mixing chamber and diffuser, the primary nozzle functioning mainly as a super charger and the secondary nozzle functioning mainly as a mixer and which furnishes a major portion of the kinetic energy for the compression work taking place in the diffuser, each nozzle being supplied with a part of the motive fluid, wherein the motive fluid supplied to the secondary nozzle has a higher pressure than that supplied to the primary nozzle and wherein the amount of motive fluid supplied to the primary nozzle is only a small part of the total motive fluid supplied to the apparatus.

Description

United States Patent 1 51 3,694,107 Stein 1 51 Sept. 26, 1972 [5 1 EJECTOR APPARATUS AND METHOD 1,175,461 3/ 1916 Leblanc ..417/ 167 OF UTILIZING SAME 1,495,150 5/1924 Bancel et al. ..417/167 [72] Inventor: Robert Stein, Rego Park, N.Y 2,000,762 5/1935 Kraft ..417/167 [73] Assignee: Nash Engineering Company, South Primary Examiner-Carlton R. Croyle Norwalk, Conn. Assistant Examiner-Richard E. Gluck 22 Filed: Nov. 19, 1910 Nlte 211 App]. No.2 90,975 TRACT Related U S Application Data A compound ejector apparatus comprising a primary nozzle, primary mixing chamber, secondary nozzle, [63] Continuation-impart of Ser. No. 44,962, June secondary mixing chamber and diffuser, the primary 10, 1970, abandoned. nozzle functioning mainly as a super charger and the secondary nozzle functioning mainly as a mixer and [52] US. Cl. ..417/167, 417/168, 417/169, which furnishes a major portion of the kinetic energy 417/180 for the compression work taking place in the diffuser, 51 1m. 01 ..F04f 5/22, F04f 5/46 each nozzle being Supplied with a P of the motive 58 Field of Search ..417/167, 168, 169, 179, 165, fluid, wherein the motive fluid supplied to the secon- 4l7/l80 dary nozzle has a higher pressure than that supplied to the primary nozzle and wherein the amount of motive fluid supplied to the primary nozzle is only a small [56] References Cited part of the total motive fluid supplied to the ap- UNITED STATES PATENTS P 1,215,321 2/1917 Leblanc ..417/167 3 Claims, 7 Drawing Figures PATENTED SEP 2 6 I972 SHEET 1 [IF 3 N OI INVENTOR ROBERT STEIN BY 7Mzi 7M6 ATTORNEYS PATENTEDSEPZB \972 SHEET 2 BF 3 INVENTOR ROBERT STEIN BY ma ima ATTORNEYS PATENTEDSEP25 I972 SHEET 3 [IF 3 INVENTOR ROBERT STEIN ATTORNEYS EJECTOR APPARATUS AND METHOD OF UTILIZING SAME The present application is a continuation-impart of copending application Ser. No. 44,962, filed on June 10, 1970, now abandoned.

The present invention relates to an ejector apparatus and more particularly to a method and apparatus of improved efficiency.

When a fluid of high potential energy, hereinafter called motive fluid, passes through a converging or converging-diverging nozzle and discharges into a space filled with another fluid of lower potential energy, hereinafter called pumped fluid, the pressure of the motive fluid is reduced while its velocity greatly increases. The motive fluid may be, for example, high pressure steam, the pumped fluid may be low pressure steam, hereinafter called vapor, flowing from an evaporator. The pressure of the fluid stream, i.e., the motive steam continues to decrease after leaving the nozzle, the pressure falling below the evaporator pressure. The difference between the pressure of the pumped fluid (vapor) and the pressure of the fluid stream of the motive steam induces a flow of vapor into the fluid stream. The penetration of the vapor particles into the fluid stream can be compared to the phenomenon of diffusion inasmuch as a vapor particle must continually displace new particles of the fluid stream in order to advance into the fluid stream. This is because the vapor does not penetrate into a stationary medium but into a fluid stream having a high velocity which is moving perpendicularly to the direction of the penetration of the vapor. The velocity of the vapor flowing toward the motive fluid stream is far below the velocity of the fluid stream as the difference between the enthalpy of the vapor and the enthalpy of the fluid stream which is the potential difference producing the flow of vapor, is much smaller than the enthalpy difference which produces the fluid stream, namely the difference between the enthalpy of the high pressure stream and the enthalpy of the low pressure vapor. The velocity of penetration, accordingly similar to the velocity of diffusion, is low. Consequently, the vapor penetrates into only a thin surface layer of the fluid stream. The core of the fluid stream is not penetrated at all or barely reached and is as a result substantially inactive, i.e., it does not contribute substantially tothe compression work. In fact it constitutes merely ballast. Thus the higher the velocity of the fluid stream, the thinner will be the vapor carrying layer of the fluid stream and the larger will be the inactive core.

The penetration of the low velocity vapor particles into the outer layer of the motive fluid stream results in a reduction of the velocity of that outer layer in the direction of flow while the velocity of the inner core of the motive fluid stream remains substantially the same. The resultant uneven velocity gradient across the fluid stream contributes to turbulence and, accordingly, to losses in kinetic energy.

It is, therefore, an object of the present invention to provide a method and apparatus for substantially reducing the velocity variations over the cross section of a fluid stream containing vapor particles.

It is a further object of the present invention to divide the plural functions normally performed by a single ejector and to provide a compound ejector including a primary nozzle which will perform primarily as a supercharger and a secondary nozzle which will perform primarily as a mixer and which will function to furnish the major part of the kinetic energy for the compression work.

These and further objects and advantages of the invention will become apparent from a consideration of the disclosure which follows.

The invention is illustrated by way of example in the accompanying drawing which forms a part of this application and in which:

FIG. 1 is an elevational cross sectional view of an embodiment of an ejector apparatus made in accordance with the teachings of the present invention;

FIG. 2 is an elevational cross sectional view of a further embodiment of an ejector apparatus made in accordance with the teachings of the present invention;

FIG. 3 is an elevational cross sectional view of a further embodiment of the invention;

FIG. 4 is an elevational cross sectional view of a further embodiment of the invention;

FIG. 5 is an elevational cross sectional view of a portion of a further embodiment of the invention;

FIG. 6 is an elevational cross sectional view of a portion of a further embodiment of the invention; and

FIG. 7 is an elevational cross sectional view of yet a further embodiment of the invention.

Referring to the drawings and more particularly to FIG. 1, a source of motive high-pressure fluid, as, for example saturated steam at psia, is diagrammatically illustrated at 10. A portion of this high pressure fluid, hereinafter referred to as motive fluid, is directed via conduit 12 to the primary nozzle 16. While FIG. 1 shows an ejector having a single nozzle 16, it is understood that this single nozzle can be replaced by a number of smaller nozzles of similar design. Such an ejector having a plurality of small nozzles has the advantage that it has a better efficiency than an ejector of the same capacity having just one large nozzle. The motive fluid leaves the primary nozzle 16 as a high velocity fluid stream 17 and has a low pressure for example of 0.15 psia. On passage through the nozzle the fluid stream will no longer be saturated i.e., the stream will have a moisture content of approximately 17 percent. The velocity of the motive fluid stream 17 leaving nozzle 16 can be calculated from the formula v=223.8/h, h,ft./sec.

where h is the enthalpy of the motive high pressure fluid at its entry into the primary nozzle 16 and h is the enthalpy of the motive fluid stream 17 leaving the primary nozzle 16. In the instant embodiment, the velocity would be approximately equal to 3,800 ft./sec. (h 119BTU, h =900BTU). After the motive fluid stream 17 has been discharged from the primary nozzle 16, the fluid stream pressure will continue to decrease.

The primary nozzle 16 discharges the fluid stream into primary mixing chamber 18. A second fluid 21 comprising the so-called pumped fluid, in this example vapor, is supplied from a second fluid source in this case an evaporator diagrammatically and partially illustrated at 20. As just noted above, after the motive fluid is discharged from the nozzle 16 its velocity further increases and as a result its pressure falls below the evaporator pressure. The resultant pressure differential induces a flow of vapor designated in the drawing by the reference numeral 21 into the motive fluid stream 17 causing particles of vapor 21 to penetrate into the motive fluid stream 17. As this pressure differential is generally small, the velocity of the vapor 21 is far lower than the velocity of the motive fluid stream 17 passing through the mixing chamber. The time available for the vapor to penetrate into the motive fluid stream is very short because as soon as the vapor penetrates into the outer layer of the motive fluid stream 17 it is carried away. Thus, for example, with a distance of two feet from the end of the first ejector nozzle 16 to the point where the penetration ends and with a motive fluid stream velocity of only 2,500 ft./sec., this period of timeof travel will amount to approximately 0.0008 seconds. Accordingly, the particles penetrate only into a very thin surface layer 26 of the motive fluid stream 17 and do not enter into the core 25. it is clear that the higher the velocity of the fluid stream 17 discharged from the primary nozzle 16 the thinner will be the vapor carrying layer and the larger will be the inactive core.

At the exit from the mixing chamber 18 there is arranged so as to annularly surround the stream 17, an annular chamber 30, which may be provided with either a single ring shaped nozzle 31 as illustrated or which may have a plurality of simple nozzles arranged in a circle concentric to the motive fluid stream path. A third fluid stream 29 which also constitutes motive fluid and which may be identical to the first fluid stream in composition and which, therefore, will have identical physical characteristics to that of the first fluid stream prior to the diversion thereof into separate conduits for introduction into the primary or secondary nozzle but which has a higher pressure as supplied to the secondary nozzle through a conduit 32 from the source con taining the motive high pressure fluid. The secondary nozzle is arranged to discharge this third fluid stream so that it will angularly intersect the fluid stream as composed of first fluid (motive) having second fluid (pumped) entrained in the outer layer thereof. The two converging fluid streams will undergo ready and thorough intermixing.

The reason for this is that the penetrating force of a fluid stream is a function of the total pressure (velocity pressure plus static pressure of that stream) while the resistance to penetration is a function only of the static pressure of the fluid stream being penetrated. This applies: (a) to the surface layer 26 of the first fluid stream 17 coming from the primary nozzle 16 and penetrating into the third fluid stream 29 of the secondary nozzle 31, (b) the core of the first fluid stream 17 coming from the primary nozzle 16 and penetrating into the third fluid stream 29 of the secondary nozzle 31, and (c) the third fluid stream 29 of the secondary nozzle 31, penetrating into the entirety of the first fluid stream 17 coming from the primary nozzle 16. By ejecting the third fluid stream 29 so that it converges at an angle with the motive fluid stream 17 an intense interaction between the two streams will result thereby ensuring a homogeneous mixture "and a very small velocity gradient across the fluid stream. The converging, but almost parallel flow of the first and third fluid streams is a factor which aids the interaction as the time available for mixing is made longer.

The compound ejector comprising a primary and a secondary nozzle in accordance with the invention permits higher compression ratios by the simple measure of increasing the pressure of the motive fluid supplied to the secondary nozzle while supplying the primary nozzle with a motive fluid of lower pressure. This difference in pressure can be brought about very simply by lowering the pressure of the motive fluid for the primary nozzle. This can be carried out manually or by means of a pressure reducing valve.

In accordance with a preferred embodiment of the invention, a pressure reducing valve 36 is provided in the conduit 12 leading from the motive fluid source 10 to the primary nozzle 16 for use in lowering the pressure of the motive fluid being supplied to the primary nozzle.

With a reduction of the motive fluid pressure, the velocity of the fluid stream discharged from the primary nozzle will be reduced permitting a longer period of time for the vapor in the mixing chamber to penetrate into the fluid stream. Accordingly, a reduction in this pressure within certain limits acts to increase the carrying capacity of the motive fluid stream. Further, by reducing the pressure of the motive fluid stream which is being directed to the primary nozzle, the relative velocity between the motive fluid stream and the vapor particles will be reduced and the shocks resulting from the high velocity fluid stream particles striking against the low velocity vapor particles will also be reduced and therewith a corresponding reduction in the loss of kinetic energy will take place.

As the loss by shock is a quadratic function of the difference of the velocities producing the shock, even a small reduction in the difference of the velocities results in a significant reduction of the loss.

Preferably, the apparatus in accordance with the invention can be modified in such a way that the pumped fluid (vapor) is admitted to the second mixing chamber 24 permitting vapor 21 to penetrate into the third fluid stream 29. This measure serves to increase the total carrying capacity of the motive fluid stream while still achieving good mixing in the second mixing chamber 24 as is shown in FIG. 3.

As can be appreciated the conventional two stage ejector apparatus utilizes first and second stage ejectors in series each of the ejectors handling the respective pumped fluid at rest (or having a very low velocity) and there is no division of functions between the first stage and second stage ejector and, consequently, each ejector works under unfavorable conditions and at a low efficiency. The present compound ejector apparatus divides the functions which are performed in duplicate by the conventional two stage ejectors, with the primary nozzle in accordance with the invention functioning mainly as supercharger while the secondary acts primarily as a mixerand supplies the major part of the energy required for the compression work. Each nozzle can accordingly be designed to fulfill its specific function and can be fed independently of the other by a motive fluid having the most convenient pressure or enthalpy.

The apparatus in accordance with the invention therefore permits higher compression ratios by the simple expedient of introducing the motive fluid into the secondary nonle at a higher pressure than that which is used for the introduction of the motive fluid into the primary nozzle. This does not in any way adversely affect the carrying capacity of the motive fluid as the pressure of the fluid stream introduced into the primary nozzle can be kept sufiiciently low. It can, therefore, be appreciated that in the ejector apparatus in accordance with the teachings of the present invention each nozzle performs a separate function which in combination achieve an outstanding amount of work as compared to the conventional arrangements.

For very high compression ratios requiring multistage compression, additional stages can be added to the compound secondary ejector. It is important to locate such additional stages at such points of the diffuser that the velocity of the fluid stream is still high enough that considerable losses by shocks are avoided. The design of the nozzle of a second or third stage ejector is similar to the design of a secondary nozzle of a compound ejector as for example illustrated in FIG. 4.

The greater the difference between the pressure in the evaporator and the motive fluid stream leaving the primary nozzle, the greater will be the velocity of the vapor and the greater will be the amount of vapor penetrating into the fluid stream. In other words, an increased over expansion increases the carrying capacity of the motive fluid stream. Over expansion cannot be carried too far because of the danger of shock which would then result in undesirable losses in kinetic energy. This danger increases with an increase in the motive fluid stream velocity and to be more precise with an increasing difference between the motive fluid stream velocity and the velocity of the pumped fluid vapor particles in the direction of flow. At lower velocities of the motive fluid stream, a'higher degree of over expansion can be tolerated and this increases the utility of the present ejector apparatus as it can then use lower pressure motive fluid for the primary nozzle than can the conventional ejectors working against the same back pressure.

The same consideration applies to the secondary nozzle, The second fluid stream, i.e., fluid to be pumped is accelerated by the motive fluid stream discharged from the primary nozzle and thus the difference between the velocity of the first fluid stream carrying entrained second fluid and the velocity of the third fluid stream discharged from the secondary nozzle is reduced permitting higher over expansion.

FIG. 2 illustrates another embodiment of the invention wherein the secondary noule 31 does not concentrically surround the motive fluid stream 17 leaving the primary nozzle, but is comprised of a single nozzle which directs a motive fluid stream 29' to converge with the fluid stream 17' with the result that the vectorial forces of the converging fluid streams modify the direction of the mixture toward the diffuser.

As can be seen from FIG. 3, it is not necessary to have two separate feeds from the evaporator since the annular chamber 30 may be suspended from the upper portion of the apparatus thereby enabling a single feed to supply the pumped fluid 24 to the motive fluid stream 17.

Additionally, while the primary nozzle 16 and its corresponding nozzle 31 can be spaced along the path of flow as illustrated in FIGS. 1-4, it is also possible as is illustrated in the portion of the ejector apparatus shown in FIG. 5, for the primary nozzle 16 to be positioned so it surrounds the secondary noule 31 both cooperating to produce a converging homogenous fluid mixture entering the diffuser 24. The function of the ejector is the same with jets of the primary nozzle 16 accomplishing the entrainment of the vapor portion, and the jets of the secondary nozzle 31 accomplishing the work of compression. In this embodiment there is only a single mixing chamber 18.

FIGS. 6-7 illustrate two additional forms of the ejector. In FIG. 6 the first stage ejector comprises a nozzle 16 a mixing chamber 18 and a diffuser 50. Reduced steam pressure is used for the first stage and full steam pressure is used for the second stage ejector. The structure illustrated in FIG. 7 is substantially the same as that illustrated in FIG. 6 with the jets of the second stage ejector shown positioned to discharge fluid stream 29 to angularly intersect the fluid stream 17 of the first stage ejector.

It can be appreciated that the ejector apparatus made in accordance with the teachings of the present invention can utilize a gas and/or a liquid as the motive and pumped fluids.

The present ejector apparatus can be utilized in steam jet refrigeration systems, vacuum pumps, and gas ejectors as well as in many other similar applications.

What is claimed is:

1. An ejector apparatus comprising a source of motive fluid, primary nozzle means, means for supplying a portion of said motive fluid at a first pressure to said primary nozzle means, said primary nozzle means comprising means for discharging said motive fluid into a converging mixing chamber means as a first fluid stream having a reduced second pressure, means for supplying a second fluid stream to be pumped to said chamber means at a pressure greater than said second pressure whereby a portion of said second fluid stream will become entrained in said first fluid stream secondary nozzle means, means for supplying a further portion of said motive fluid at a third pressure greater than said first pressure to said secondary nozzle means, said secondary nozzle means comprising means for discharging said motive fluid as a third fluid stream to angularly intersect said first fluid stream with a portion of said second stream entrained therein within said chamber means thereby to effect mixing of said third fluid stream and first fluid streams with said second fluid stream entrained in it, said chamber means being substantially continuously converging between the nozzles whereby the velocity of said first fluid stream with a portion of said second stream entrained therein and the pressure thereof is maintained substantially constant, said secondary nozzle producing the major portion of the total kinetic energy necessary to produce the compression work by said apparatus and said primary nozzle producing but a minor portion of said total kinetic energy said mixing chamber issuing directly to a diffuser.

2. An ejector apparatus according to claim 1, wherein said secondary nozzle means includes an annular nozzle concentrically surrounding said first fluid stream.

3. An ejector apparatus comprising a source of motive fluid, primary nozzle means connected to said source, a converging mixing chamber means, said primary nonle means constituting means for delivering a stream of motive fluid to said chamber means at a first pressure, conduit means supplying a stream of fluid to be pumped to said mixing chamber means at a second pressure higher than said first pressure whereby fluid to be pumped is entrained in said motive fluid stream from said primary nozzle to constitute therewith a primary fluid stream, secondary nozzle means delivering a second stream of motive fluid, said secondary nozzle means being angularly inclined to said primary fluid stream and issuing into said mixing chamber to intercept the primary fluid stream and to include between the primary stream and the second motive fluid stream an acute angle said chamber means being substantially continuously converging between the nozzles whereby the velocity of said first fluid stream with a portion of said second stream entrained therein and the pressure thereof are maintained substantially constant whereby said second motive fluid stream combines with said primary fluid stream, said mixing chamber issuing directly to a diffuser the motive fluid being delivered to said primary nozzle at a lesser pressure than to said secondary nozzle.

. l l l I

Claims (3)

1. An ejector apparatus comprising a source of motive fluid, primary nozzle means, means for supplying a portion of said motive fluid at a first pressure to said primary nozzle means, said primary nozzle means comprising means for discharging said motive fluid into a converging mixing chamber means as a first fluid stream having a reduced second pressure, means for supplying a second fLuid stream to be pumped to said chamber means at a pressure greater than said second pressure whereby a portion of said second fluid stream will become entrained in said first fluid stream secondary nozzle means, means for supplying a further portion of said motive fluid at a third pressure greater than said first pressure to said secondary nozzle means, said secondary nozzle means comprising means for discharging said motive fluid as a third fluid stream to angularly intersect said first fluid stream with a portion of said second stream entrained therein within said chamber means thereby to effect mixing of said third fluid stream and first fluid streams with said second fluid stream entrained in it, said chamber means being substantially continuously converging between the nozzles whereby the velocity of said first fluid stream with a portion of said second stream entrained therein and the pressure thereof is maintained substantially constant, said secondary nozzle producing the major portion of the total kinetic energy necessary to produce the compression work by said apparatus and said primary nozzle producing but a minor portion of said total kinetic energy said mixing chamber issuing directly to a diffuser.
2. An ejector apparatus according to claim 1, wherein said secondary nozzle means includes an annular nozzle concentrically surrounding said first fluid stream.
3. An ejector apparatus comprising a source of motive fluid, primary nozzle means connected to said source, a converging mixing chamber means, said primary nozzle means constituting means for delivering a stream of motive fluid to said chamber means at a first pressure, conduit means supplying a stream of fluid to be pumped to said mixing chamber means at a second pressure higher than said first pressure whereby fluid to be pumped is entrained in said motive fluid stream from said primary nozzle to constitute therewith a primary fluid stream, secondary nozzle means delivering a second stream of motive fluid, said secondary nozzle means being angularly inclined to said primary fluid stream and issuing into said mixing chamber to intercept the primary fluid stream and to include between the primary stream and the second motive fluid stream an acute angle said chamber means being substantially continuously converging between the nozzles whereby the velocity of said first fluid stream with a portion of said second stream entrained therein and the pressure thereof are maintained substantially constant whereby said second motive fluid stream combines with said primary fluid stream, said mixing chamber issuing directly to a diffuser the motive fluid being delivered to said primary nozzle at a lesser pressure than to said secondary nozzle.
US3694107A 1970-11-19 1970-11-19 Ejector apparatus and method of utilizing same Expired - Lifetime US3694107A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US9097570 true 1970-11-19 1970-11-19

Publications (1)

Publication Number Publication Date
US3694107A true US3694107A (en) 1972-09-26

Family

ID=22225187

Family Applications (1)

Application Number Title Priority Date Filing Date
US3694107A Expired - Lifetime US3694107A (en) 1970-11-19 1970-11-19 Ejector apparatus and method of utilizing same

Country Status (1)

Country Link
US (1) US3694107A (en)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885891A (en) * 1972-11-30 1975-05-27 Rockwell International Corp Compound ejector
DE2541439A1 (en) * 1975-09-17 1977-04-21 Specializirovannyj Trest Proiz Ejector pump with mixing chamber - has injector ducts in two planes and inclined to produce eddy and downstream injection stage
US4396355A (en) * 1980-01-28 1983-08-02 United Kingdom Atomic Energy Authority Ejector
US4448354A (en) * 1982-07-23 1984-05-15 The United States Of America As Represented By The Secretary Of The Air Force Axisymmetric thrust augmenting ejector with discrete primary air slot nozzles
DE3636235A1 (en) * 1985-10-24 1987-04-30 Erich Sterzel Nozzle arrangement for generating a directed flow
WO1991015722A1 (en) * 1990-04-10 1991-10-17 Masur, Walter Process for operating a compression heat pump and compression heat pump
WO2001092728A1 (en) * 2000-06-02 2001-12-06 Airvac Services (S) Pte Ltd. A pump system
US6345234B1 (en) * 1997-11-12 2002-02-05 Fisher Controls International, Inc. Fugitive emission sensing system
US6382321B1 (en) 1999-09-14 2002-05-07 Andrew Anderson Bates Dewatering natural gas-assisted pump for natural and hydrocarbon wells
US20070256420A1 (en) * 2006-05-04 2007-11-08 Schott Carl G Methods and apparatus for assembling a low noise ejector motive nozzle
US20090297339A1 (en) * 2008-05-29 2009-12-03 General Electric Company Low noise ejector for a turbomachine
US20100162732A1 (en) * 2008-12-30 2010-07-01 Linde, Inc. Cooling or Freezing Apparatus Using High Heat Transfer Nozzle
US20100255386A1 (en) * 2009-04-07 2010-10-07 Helpful Technologies, Inc. Method and system for anode gas recirculation in fuel cells
WO2014094890A1 (en) * 2012-12-21 2014-06-26 Xerex Ab Vacuum ejector nozzle with elliptical diverging section
WO2014094878A1 (en) * 2012-12-21 2014-06-26 Xerex Ab Vacuum ejector with multi-nozzle drive stage
CN105051376A (en) * 2012-12-21 2015-11-11 谢雷克斯公司 Vacuum ejector with multi-nozzle drive stage and booster
WO2016062610A1 (en) * 2014-10-20 2016-04-28 Ksb Aktiengesellschaft Jet pump
WO2018012987A1 (en) * 2016-07-13 2018-01-18 Fjord Flow As Combined jacket ejector and centre ejector pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1175461A (en) * 1914-05-05 1916-03-14 Expl Des Procedes Westinghouse Leblanc Sa Ejector.
US1215321A (en) * 1915-06-22 1917-02-06 Expl Des Procedes Westinghouse Leblanc Sa Ejector.
US1495150A (en) * 1922-08-18 1924-05-27 Ingersoll Rand Co Jet augmenter or ejector
US2000762A (en) * 1933-10-26 1935-05-07 Gen Electric Fluid jet pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1175461A (en) * 1914-05-05 1916-03-14 Expl Des Procedes Westinghouse Leblanc Sa Ejector.
US1215321A (en) * 1915-06-22 1917-02-06 Expl Des Procedes Westinghouse Leblanc Sa Ejector.
US1495150A (en) * 1922-08-18 1924-05-27 Ingersoll Rand Co Jet augmenter or ejector
US2000762A (en) * 1933-10-26 1935-05-07 Gen Electric Fluid jet pump

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885891A (en) * 1972-11-30 1975-05-27 Rockwell International Corp Compound ejector
DE2541439A1 (en) * 1975-09-17 1977-04-21 Specializirovannyj Trest Proiz Ejector pump with mixing chamber - has injector ducts in two planes and inclined to produce eddy and downstream injection stage
US4396355A (en) * 1980-01-28 1983-08-02 United Kingdom Atomic Energy Authority Ejector
US4448354A (en) * 1982-07-23 1984-05-15 The United States Of America As Represented By The Secretary Of The Air Force Axisymmetric thrust augmenting ejector with discrete primary air slot nozzles
DE3636235A1 (en) * 1985-10-24 1987-04-30 Erich Sterzel Nozzle arrangement for generating a directed flow
WO1991015722A1 (en) * 1990-04-10 1991-10-17 Masur, Walter Process for operating a compression heat pump and compression heat pump
US6345234B1 (en) * 1997-11-12 2002-02-05 Fisher Controls International, Inc. Fugitive emission sensing system
US6382321B1 (en) 1999-09-14 2002-05-07 Andrew Anderson Bates Dewatering natural gas-assisted pump for natural and hydrocarbon wells
WO2001092728A1 (en) * 2000-06-02 2001-12-06 Airvac Services (S) Pte Ltd. A pump system
US20070256420A1 (en) * 2006-05-04 2007-11-08 Schott Carl G Methods and apparatus for assembling a low noise ejector motive nozzle
US8474270B2 (en) 2006-05-04 2013-07-02 General Electric Company Methods and apparatus for assembling a low noise ejector motive nozzle
US8136361B2 (en) 2006-05-04 2012-03-20 General Electric Company Methods and apparatus for assembling a low noise ejector motive nozzle
US20090297339A1 (en) * 2008-05-29 2009-12-03 General Electric Company Low noise ejector for a turbomachine
US20100162732A1 (en) * 2008-12-30 2010-07-01 Linde, Inc. Cooling or Freezing Apparatus Using High Heat Transfer Nozzle
US7992393B2 (en) * 2008-12-30 2011-08-09 Linde Aktiengesellschaft Cooling or freezing apparatus using high heat transfer nozzle
US20100255386A1 (en) * 2009-04-07 2010-10-07 Helpful Technologies, Inc. Method and system for anode gas recirculation in fuel cells
US8672643B2 (en) * 2009-04-07 2014-03-18 Helpful Alliance Company Method and system for anode gas recirculation in fuel cells
WO2014094890A1 (en) * 2012-12-21 2014-06-26 Xerex Ab Vacuum ejector nozzle with elliptical diverging section
WO2014094878A1 (en) * 2012-12-21 2014-06-26 Xerex Ab Vacuum ejector with multi-nozzle drive stage
CN105026772A (en) * 2012-12-21 2015-11-04 谢雷克斯公司 Vacuum ejector nozzle with elliptical diverging section
CN105051376A (en) * 2012-12-21 2015-11-11 谢雷克斯公司 Vacuum ejector with multi-nozzle drive stage and booster
CN105074228A (en) * 2012-12-21 2015-11-18 谢雷克斯公司 Vacuum ejector with multi-nozzle drive stage
US20150337866A1 (en) * 2012-12-21 2015-11-26 Xerex Ab Vacuum Ejector With Multi-Nozzle Drive Stage
US20150354601A1 (en) * 2012-12-21 2015-12-10 Xerex Ab Vacuum Ejector Nozzle With Elliptical Diverging Section
WO2016062610A1 (en) * 2014-10-20 2016-04-28 Ksb Aktiengesellschaft Jet pump
WO2018012987A1 (en) * 2016-07-13 2018-01-18 Fjord Flow As Combined jacket ejector and centre ejector pump

Similar Documents

Publication Publication Date Title
US3667221A (en) Fuel delivery apparatus
US3561195A (en) Gas purifying device
US3616596A (en) Process and device for the separation of molecules of different masses
US3169367A (en) Combustion apparatus
US3381471A (en) Combustion chamber for gas turbine engines
US3016063A (en) Fluid valve
US3387895A (en) Non-clogging splitter unit for dividing the flow of fluid-conveyed material
US4332529A (en) Jet diffuser ejector
US3795259A (en) Device for evenly mixing and distributing a gas and liquid mixture
US2520388A (en) Apparatus for supporting combustion in fast-moving air streams
US4867918A (en) Gas dispersion process and system
US6072820A (en) Chemical oxygen iodine laser gain generator system
US3570242A (en) Fuel premixing for smokeless jet engine main burner
US2375180A (en) Apparatus for jet propulsive and other purposes
US3032988A (en) Jet reaction turbine
US5390450A (en) Supersonic exhaust nozzle having reduced noise levels for CO2 cleaning system
US4037991A (en) Fluid-flow assisting devices
US3485566A (en) Burner for firing a combustion chamber
US4046492A (en) Air flow amplifier
US3852409A (en) Process for the removal of particulate matter and acidic gases from carrier gases
US5992529A (en) Mixing passage in a foam fire fighting nozzle
US2679137A (en) Apparatus for burning fuel in a fast moving gas stream
US3826083A (en) Recirculating combustion apparatus jet pump
US3134229A (en) Combustion chamber
US2981066A (en) Turbo machine